JPS628453Y2 - - Google Patents
Info
- Publication number
- JPS628453Y2 JPS628453Y2 JP1982013383U JP1338382U JPS628453Y2 JP S628453 Y2 JPS628453 Y2 JP S628453Y2 JP 1982013383 U JP1982013383 U JP 1982013383U JP 1338382 U JP1338382 U JP 1338382U JP S628453 Y2 JPS628453 Y2 JP S628453Y2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- spider
- intermediate shaft
- attached
- gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 241000239290 Araneae Species 0.000 claims description 29
- 230000005540 biological transmission Effects 0.000 claims description 11
- 230000007935 neutral effect Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. a stepped orbital gear or Ravigneaux
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Structure Of Transmissions (AREA)
- Arrangement Of Transmissions (AREA)
- Arrangement Or Mounting Of Control Devices For Change-Speed Gearing (AREA)
Description
【考案の詳細な説明】
本考案は、遊星伝動装置を用いたギヤトランス
ミツシヨンに関し、その目的は、安価、簡単な構
造で、前進状態において最大６段、後進状態にお
いて最大２段の変速を行なえるようにする点にあ
る。[Detailed description of the invention] The present invention relates to a gear transmission using a planetary transmission.The purpose of the invention is to have a low cost, simple structure, and to be able to shift up to 6 speeds in the forward state and up to 2 speeds in the reverse state. The point is to make it possible to do so.
以上要するに、本考案によるギヤトランスミツ
シヨンの特徴構成は、入力軸２０、第１中間軸２
１及び第２中間軸２２を同芯状に配置し、前記第
１中間軸２１に後進用筒軸２３をかつ前記第２中
間軸２２に出力用筒軸２４を夫々相対回転自在に
取付け、スパイダー２５の両端を前記両筒軸２
３，２４に各別にかつ相対回転自在に取付け、前
記入力軸２０と第１中間軸２１の間に第１クラツ
チ２６を、前記入力軸２０と後進用筒軸２３の間
に第２クラツチ２７を、かつ、前記第２中間軸２
２と出力用筒軸２４の間に第３クラツチ２８を
夫々設け、前記第１及び第２中間軸２１及び２２
に各別に固着した第１及び第２外歯ギヤ２１ａ及
び２２ａに各別に常時咬合する第３及び第４外歯
ギヤ２９及び３０を前記スパイダー２５に相対回
転自在に取付け、前記両筒軸２３，２４に各別に
固着した第５及び第６外歯ギヤ２３ａ及び２４ａ
に各別に咬合すると共に前記第３及び第４外歯ギ
ヤ２９及び３０に各別に咬合する第７及び第８外
歯ギヤ３１及び３２を前記スパイダー２５に相対
回転自在に取付け、前記後進用筒軸２３に対する
第１ブレーキ３３、前記第３外歯ギヤ２９に常時
咬合する内歯ギヤ３４に対する第２ブレーキ３
５、及び、前記第２中間軸２２に対する第３ブレ
ーキ３６を設け、前記第１ないし第３クラツチ２
６，２７，２８及び第１ないし第３ブレーキ３
３，３５，３６を選択操作する変速操作装置を設
けてある。 In summary, the characteristic configuration of the gear transmission according to the present invention is that the input shaft 20, the first intermediate shaft 2
The first intermediate shaft 22 and the second intermediate shaft 22 are arranged concentrically, and the reverse cylinder shaft 23 is attached to the first intermediate shaft 21 and the output cylinder shaft 24 is relatively rotatably attached to the second intermediate shaft 22. Both ends of 25 are connected to the double cylinder shaft 2
3 and 24 separately and relatively rotatably, a first clutch 26 is disposed between the input shaft 20 and the first intermediate shaft 21, and a second clutch 27 is disposed between the input shaft 20 and the reverse cylinder shaft 23. , and the second intermediate shaft 2
A third clutch 28 is provided between the output cylinder shaft 24 and the first and second intermediate shafts 21 and 22, respectively.
Third and fourth external gears 29 and 30, which are in constant engagement with the first and second external gears 21a and 22a, which are respectively fixed to the spider 25, are attached to the spider 25 so as to be relatively rotatable. 5th and 6th external gears 23a and 24a respectively fixed to 24
Seventh and eighth external gears 31 and 32, which engage with the third and fourth external gears 29 and 30, respectively, are attached to the spider 25 so as to be relatively rotatable. 23, and a second brake 3 for the internal gear 34 that is always engaged with the third external gear 29.
5, and a third brake 36 for the second intermediate shaft 22, and the first to third clutches 2
6, 27, 28 and first to third brakes 3
A gear shift operation device for selectively operating gears 3, 35, and 36 is provided.
すなわち、外歯ギヤに較べて高価な内歯ギヤ３
４を１つにし、しかも、スパイダー２５を１つだ
けで済ませるようにして、複数のスパイダーを用
いた場合に、それの支持のために構造が複雑化し
て高価になることを抑制させるようにしてあるか
ら、安価、簡単な構造で、前進状態において最大
６段、後進状態において最大２段の変速を行なわ
せることができるのであり、もつて、実用上の利
点大なギヤトランスミツシヨンを得るに至つた。 In other words, the internal gear 3 is more expensive than the external gear.
4 into one, and only one spider 25 is required, so that when a plurality of spiders are used, the structure is not complicated and expensive to support them. Because of this, it is possible to achieve a gear transmission with a simple and inexpensive structure that can shift up to 6 gears in forward motion and up to 2 gears in reverse. I've reached it.
次に、本考案の実施例を図面に基づいて説明す
る。 Next, embodiments of the present invention will be described based on the drawings.
第１図に示すように、駆動回転可能な左右前輪
１，１を備えるとともに、油圧シリンダ２ａにて
対車体上下揺動操作可能なアーム２、及び、油圧
シリンダ３ａにて対アーム上下揺動操作可能なバ
ケツト３等からなるフロントローダ装置４を備え
た前部車体を設ける一方、駆動回転可能な左右後
輪５，５を備えるとともに、運転席６の下方にエ
ンジン７を搭載し、走行用ミツシヨンケース８を
エンジン７の前部に接続し、エンジン７の後方
に、ラジエータ９を設け、さらに、対車体左右ス
ライド調節自在で且つ対車体左右揺動自在な取付
台１０、油圧シリンダ１１ａにて対取付台上下揺
動操作可能なブーム１１、油圧シリンダ１２ａに
て対ブーム上下揺動操作可能なアーム１２、油圧
シリンダ１３ａにて対アーム上下揺動操作可能な
バケツト１３等からなるバツクホウ装置１４を、
運転席６の後方に設けた後部車体を設け、そし
て、前部車体と後部車体とを上下軸心Ｘ周りに回
転自在に枢支し、両車体を屈折揺動操作する左右
油圧シリンダ１５，１５を両車体間に架設し、左
右油圧シリンダ１５，１５を背反的に伸縮作動さ
せるためのオービツトロール１６を回転操作する
ステアリングハンドル１７を後部車体に設け、そ
して、運転席６を前後に向き変更可能に取付ける
とともに、運転席６の前方及び後方夫々に、フロ
ントローダ装置４に対する操作部４Ａ、バツクホ
ウ装置１４に対する操作部１４Ａを設け、もつ
て、運転席６を前向きにした状態において、土砂
を掬い取り運搬放出する作業を行ない、しかも、
運転席６を後向きにした状態において、溝等を掘
削する作業を行なう作業車を構成してある。 As shown in FIG. 1, it is equipped with left and right front wheels 1, 1 that can be driven and rotated, and an arm 2 that can be operated to swing vertically relative to the vehicle body using a hydraulic cylinder 2a, and an arm 2 that can be operated vertically swinging relative to the vehicle body using a hydraulic cylinder 3a. A front vehicle body is provided with a front loader device 4 consisting of a bucket truck 3, etc., which can drive and rotate. A radiator case 8 is connected to the front part of the engine 7, a radiator 9 is provided behind the engine 7, and a mounting base 10 that can be freely adjusted to slide horizontally relative to the vehicle body and swing freely relative to the vehicle body horizontally, and a hydraulic cylinder 11a is installed. A backhoe device 14 includes a boom 11 that can be operated to swing up and down with respect to a mounting base, an arm 12 that can be operated to swing up and down with respect to the boom with a hydraulic cylinder 12a, a bucket 13 that can be operated with a hydraulic cylinder 13a that can be operated to swing up and down with respect to the arm, etc. ,
A rear vehicle body is provided behind the driver's seat 6, and left and right hydraulic cylinders 15, 15 rotatably support the front vehicle body and the rear vehicle body around the vertical axis X, and perform bending and rocking operations of both vehicle bodies. is installed between the two vehicle bodies, and a steering handle 17 for rotating an orbiter 16 for telescopically operating the left and right hydraulic cylinders 15, 15 is provided in the rear vehicle body, and the direction of the driver's seat 6 is changed back and forth. In addition, an operating section 4A for the front loader device 4 and an operating section 14A for the backhoe device 14 are provided in front and rear of the driver's seat 6, respectively, so that soil can be scooped out with the driver's seat 6 facing forward. We carry out the work of collecting, transporting and discharging, and
The work vehicle is configured to perform work such as digging a trench with the driver's seat 6 facing rearward.
前記走行用ミツシヨンケース８内に、前進速度
を６段に、且つ、後進速度を２段に変速するギヤ
トランスミツシヨンを装備し、軸芯を前後方向に
向けた出力軸１８を、ミツシヨンケース８に貫通
支承し、出力軸１８と前後輪１，５を接続する伸
縮及び屈折可能な伝動軸１９，１９を設けてあ
る。 The traveling transmission case 8 is equipped with a gear transmission that changes the forward speed to 6 speeds and the reverse speed to 2 speeds, and an output shaft 18 whose axis is directed in the front-rear direction is connected to the transmission. Expandable and bendable transmission shafts 19 and 19 are provided which are supported through the case 8 and which connect the output shaft 18 and the front and rear wheels 1 and 5.
第２図に示すように、前記ギヤトランスミツシ
ヨンを構成するに、入力軸２０、第１中間軸２１
及び、第２中間軸２２を、前後方向に沿う状態で
同芯状に配置し、第１中間軸２１に後進用筒軸２
３をかつ第２中間軸２２に出力用筒軸２４を夫々
相対回転自在に取付け、スパイダー２５の両端が
わ円盤状部材２５ａ，２５ａを前記両筒軸２１，
２２に各別にかつ相対回転自在に取付け、前記入
力軸２０と第１中間軸２１の間に多板型の第１ク
ラツチ２６を、前記入力軸２０と後進用筒軸２３
の間に多板型の第２クラツチ２７を、かつ、前記
第２中間軸２２と出力用筒軸２４の間に第３クラ
ツチ２８を夫々設け、前記第１及び第２中間軸２
１，２２に各別に固着した第１及び第２外歯ギヤ
２１ａ，２２ａに各別に常時咬合する第３及び第
４外歯ギヤ２９，３０を前記スパイダー２５に相
対回転自在に取付け、前記両筒軸２３，２４に各
別に固着した第５及び第６外歯ギヤ２３ａ，２４
ａに各別に咬合すると共に前記第３及び第４外歯
ギヤ２９，３０に各別に咬合する第７及び第８外
歯ギヤ３１，３２を前記スパイダー２５に相対回
転自在に取付け、前記後進用筒軸２３に対する多
板型第１ブレーキ３３、前記第３外歯ギヤ２９に
常時咬合する内歯ギヤ３４に対する多板型第２ブ
レーキ３５、及び、前記第２中間軸２２に対する
第３ブレーキ３６を設け、さらに、入力軸２０
を、走行クラツチ３６及びギヤ連動機構を介して
エンジン７に連動連結し、出力用筒軸２４を、ギ
ヤ連動機構を介して前記出力軸１８に連動連結し
てある。そして、第２図及び第３図に示すよう
に、前記第１乃至第３クラツチ２６，２７，２８
の夫々に対する入り操作用油圧シリンダ２６Ａ，
２７Ａ，２８Ａ、及び、第１乃至第３ブレーキ３
３，３５，３６の夫々に対する入り操作用油圧シ
リンダ３３Ａ，３５Ａ，３６Ａを設け、それらシ
リンダ２６Ａ・・の夫々に対する電磁式制御弁２
６Ｖ，２７Ｖ，２８Ｖ，３３Ｖ，３５Ｖ，３６Ｖ
を設けるとともに、変速レバー３７を、中立位置
Ｎから前方に向つて前進１速から前進６速に相当
する位置F1，F2，F3，F4，F5，F6に切換操作可
能且つ、中立位置Ｎから後方に向つて後進１速及
び後進２速に相当する位置R1，R2に切換操作可
能に枢支した状態で設け、レバー３７の位置を電
気信号の変動として検出する装置３８を設け、更
に、検出装置３８の情報及び予め記憶された情報
に基づいて前記弁２６Ｖ・・を選択的に通電作動
をさせるマイコン利用のバルブ操作回路３９を設
け、もつて、変速レバー３７の揺動によつて、前
進６段、及び、後進２段の変速を行なえるように
構成してある。 As shown in FIG. 2, the gear transmission includes an input shaft 20, a first intermediate shaft 21,
The second intermediate shaft 22 is arranged concentrically along the front-rear direction, and the reverse cylindrical shaft 2 is attached to the first intermediate shaft 21.
3 and the output cylindrical shafts 24 are respectively attached to the second intermediate shaft 22 so as to be relatively rotatable, and the disk-shaped members 25a, 25a are attached to both ends of the spider 25 to the two cylindrical shafts 21,
A multi-plate type first clutch 26 is mounted between the input shaft 20 and the first intermediate shaft 21, and a multi-plate first clutch 26 is mounted between the input shaft 20 and the reverse cylindrical shaft 23.
A multi-plate second clutch 27 is provided between the first and second intermediate shafts 2, and a third clutch 28 is provided between the second intermediate shaft 22 and the output cylindrical shaft 24.
Third and fourth external gears 29 and 30, which are in constant engagement with the first and second external gears 21a and 22a respectively fixed to the spiders 1 and 22, are attached to the spider 25 so as to be relatively rotatable. Fifth and sixth external gears 23a and 24 respectively fixed to shafts 23 and 24
Seventh and eighth external gears 31 and 32 that engage with the third and fourth external gears 29 and 30 respectively are attached to the spider 25 so as to be relatively rotatable, and A multi-plate first brake 33 is provided for the shaft 23, a multi-plate second brake 35 is provided for the internal gear 34 that is always engaged with the third external gear 29, and a third brake 36 is provided for the second intermediate shaft 22. , furthermore, the input shaft 20
is operatively connected to the engine 7 via a travel clutch 36 and a gear interlocking mechanism, and an output cylindrical shaft 24 is operatively connected to the output shaft 18 via a gear interlocking mechanism. As shown in FIGS. 2 and 3, the first to third clutches 26, 27, 28
Hydraulic cylinder 26A for entering operation for each of
27A, 28A, and first to third brakes 3
Hydraulic cylinders 33A, 35A, 36A for entering operation are provided for each of the cylinders 3, 35, 36, and an electromagnetic control valve 2 for each of the cylinders 26A...
6V, 27V, 28V, 33V, 35V, 36V
In addition, the gear shift lever 37 can be switched forward from the neutral position N to positions F 1 , F 2 , F 3 , F 4 , F 5 , F 6 corresponding to forward 1st to 6th forward speeds. , a device that is pivotally supported so that it can be switched rearward from the neutral position N to positions R 1 and R 2 corresponding to 1st reverse speed and 2nd reverse speed, and detects the position of the lever 37 as a fluctuation in an electric signal. 38, and is further provided with a valve operation circuit 39 using a microcomputer that selectively energizes the valve 26V based on the information of the detection device 38 and information stored in advance. It is configured to be able to perform six forward speeds and two reverse speeds by swinging.
さらに詳述すると、前進１速状態では、第１ク
ラツチ２６、第２ブレーキ３５、第３クラツチ２
８を入り操作することになり、そして、第１中間
軸２１の回転力が、第３外歯ギヤ２９及び内歯ギ
ヤ３４を用いてスパイダー２５を回転させ、出力
用筒軸２４がスパイダー２５と一体回転する。 More specifically, in the first forward speed state, the first clutch 26, the second brake 35, and the third clutch 2
8, the rotational force of the first intermediate shaft 21 rotates the spider 25 using the third external gear 29 and the internal gear 34, and the output cylinder shaft 24 interacts with the spider 25. Rotates as one.
前進２速状態では、第１，第３クラツチ２６，
２８及び第１ブレーキ３３を入り操作することに
なり、第１中間軸２１の回転力が、第３，第５，
第７外歯ギヤ２９，２３ａ，３１を用いてスパイ
ダー２５を回転させ、出力用筒軸２４がスパイダ
ー２５と、一体回転する。 In the second forward speed state, the first and third clutches 26,
28 and the first brake 33, the rotational force of the first intermediate shaft 21 is applied to the third, fifth,
The spider 25 is rotated using the seventh external gears 29, 23a, and 31, and the output cylinder shaft 24 rotates integrally with the spider 25.
前進３速状態では、第１クラツチ２６、及び、
第２，第３ブレーキ３５，３６を入り操作するこ
とになり、そして、第１中間軸２１の回転力が、
前述の如くスパイダー２５を回転させ、スパイダ
ー２５の回転力が、第２，第４，第６，第８外歯
ギヤ２２ａ，３０，２４ａ，３２を用いて出力用
筒軸２４を回転させる。 In the third forward speed state, the first clutch 26 and
The second and third brakes 35 and 36 are operated, and the rotational force of the first intermediate shaft 21 is
The spider 25 is rotated as described above, and the rotational force of the spider 25 rotates the output cylinder shaft 24 using the second, fourth, sixth, and eighth external gears 22a, 30, 24a, and 32.
前進４速状態では、第１，第２，第３クラツチ
２６，２７，２８を入り操作することになり、そ
して、入力軸２０と出力用筒軸２４とを一体回転
させる。 In the fourth forward speed state, the first, second, and third clutches 26, 27, and 28 are engaged, and the input shaft 20 and the output cylinder shaft 24 are rotated together.
前進５速状態では、第１クラツチ２６、及び、
第１，第３ブレーキ３３，３６を入り操作するこ
とになり、そして、第１中間軸２１の回転力が、
前述の如くスパイダー２５を回転させ、スパイダ
ー２５の回転力が、前述の如く出力用筒軸２４を
回転させる。 In the 5th forward speed state, the first clutch 26 and
The first and third brakes 33 and 36 are operated, and the rotational force of the first intermediate shaft 21 is
The spider 25 is rotated as described above, and the rotational force of the spider 25 rotates the output cylinder shaft 24 as described above.
前進６速状態では、第１，第２クラツチ２６，
２７、及び、第３ブレーキ３６を入り操作するこ
とになり、そして、入力軸２０とスパイダー２５
とを一体回転させ、スパイダー２５の回転力が、
前述の如く出力用筒軸２４を回転させる。 In the 6th forward speed state, the first and second clutches 26,
27 and the third brake 36, and then the input shaft 20 and the spider 25
The rotational force of the spider 25 is
The output cylinder shaft 24 is rotated as described above.
後進１速状態では、第２，第３クラツチ２７，
２８、及び、第２ブレーキ３５を入り操作するこ
とになり、そして、後進用筒軸２３の回転力が、
内歯ギヤ３４、及び、第３，第４，第５外歯ギヤ
２９，３１，２３ａを用いて、スパイダー２５を
逆回転させ、スパイダー２５と出力用筒軸２４が
一体回転する。 In the first reverse gear state, the second and third clutches 27,
28 and the second brake 35 are operated, and the rotational force of the reverse cylinder shaft 23 is
The spider 25 is reversely rotated using the internal gear 34 and the third, fourth, and fifth external gears 29, 31, and 23a, and the spider 25 and the output cylinder shaft 24 are rotated together.
後進２速状態では、第２クラツチ２７、及び、
第２，第３ブレーキ３６を入り操作することにな
り、そして、後進用筒軸２３の回転力が、前述の
如くスパイダー２５を逆回転させ、スパイダー２
５の回転力が、前述の如く出力用筒軸２４を回転
させる。 In the second reverse speed state, the second clutch 27 and
The second and third brakes 36 are applied, and the rotational force of the reverse cylinder shaft 23 causes the spider 25 to reversely rotate as described above, causing the spider 25 to rotate in the opposite direction.
The rotational force of 5 rotates the output cylinder shaft 24 as described above.
本考案を実施するに、前進６段、後進２段より
も少ない段数で変速させるようにしてもよく、そ
して、前進３速と前進４速とは近い速度となるか
ら、前進３速を省略してもよい。 In implementing the present invention, the gears may be shifted in fewer gears than six forward gears and two reverse gears, and the third forward gear and the fourth forward gear are close in speed, so the third forward gear may be omitted. You can.
又、スパイダー２５を構成するに、両端がわ円
盤状部材２５ａ，２５ａを、アーム状に形成して
もよい。 Further, when configuring the spider 25, the disk-shaped members 25a, 25a at both ends may be formed into an arm shape.
又、変速操作装置を構成するに、マイコン等を
用いて電気信号にて操作する他、例えば、シリン
ダ２６Ａ…対する弁２６Ｖ…をパイロツト圧操作
式に構成し、変速レバー３７にてパイロツト圧発
生用バルブを切換操作させるようにする等、各種
構造に変更してもよい。 In addition, the gear shift operating device is operated by electric signals using a microcomputer, etc., and, for example, the valves 26V for the cylinders 26A are configured to be operated by pilot pressure, and the gear shift lever 37 is used to generate pilot pressure. The structure may be modified in various ways, such as by switching the valve.
第１図は作業車の一部切欠き側面図、第２図は
ギヤトランスミツシヨンの概略側面図、第３図は
変速操作装置のブロツク線図である。
２０……入力軸、２１……第１中間軸、２１ａ
……第１外歯ギヤ、２２……第２中間軸、２２ａ
……第２外歯ギヤ、２３……後進用筒軸、２３ａ
……第５外歯ギヤ、２４……出力用筒軸、２４ａ
……第６外歯ギヤ、２５……スパイダー、２６…
…第１クラツチ、２７……第２クラツチ、２８…
…第３クラツチ、２９……第３外歯ギヤ、３０…
…第４外歯ギヤ、３１……第７外歯ギヤ、３２…
…第８外歯ギヤ、３３……第１ブレーキ、３４…
…内歯ギヤ、３５……第２ブレーキ、３６……第
３ブレーキ。
FIG. 1 is a partially cutaway side view of the working vehicle, FIG. 2 is a schematic side view of the gear transmission, and FIG. 3 is a block diagram of the speed change operating device. 20...Input shaft, 21...First intermediate shaft, 21a
...First external gear, 22... Second intermediate shaft, 22a
...Second external gear, 23...Reverse cylinder shaft, 23a
...Fifth external gear, 24... Output cylinder shaft, 24a
...Sixth external gear, 25...Spider, 26...
...First clutch, 27...Second clutch, 28...
...Third clutch, 29...Third external gear, 30...
...Fourth external gear, 31... Seventh external gear, 32...
...Eighth external gear, 33...First brake, 34...
...Internal gear, 35...Second brake, 36...Third brake.
Claims (1)
２を同芯状に配置し、前記第１中間軸２１に後進
用筒軸２３をかつ前記第２中間軸２２に出力用筒
軸２４を夫々相対回転自在に取付け、スパイダー
２５の両端を前記両筒軸２３，２４に各別にかつ
相対回転自在に取付け、前記入力軸２０と第１中
間軸２１の間に第１クラツチ２６を、前記入力軸
２０と後進用筒軸２３の間に第２クラツチ２７
を、かつ、前記第２中間軸２２と出力用筒軸２４
の間に第３クラツチ２８を夫々設け、前記第１及
び第２中間軸２１及び２２に各別に固着した第１
及び第２外歯ギヤ２１ａ及び２２ａに各別に常時
咬合する第３及び第４外歯ギヤ２９及び３０を前
記スパイダー２５に相対回転自在に取付け、前記
両筒軸２３，２４に各別に固着した第５及び第６
外歯ギヤ２３ａ及び２４ａに各別に咬合すると共
に前記第３及び第４外歯ギヤ２９及び３０に各別
に咬合する第７及び第８外歯ギヤ３１及び３２を
前記スパイダー２５に相対回転自在に取付け、前
記後進用筒軸２３に対する第１ブレーキ３３、前
記第３外歯ギヤ２９に常時咬合する内歯ギヤ３４
に対する第２ブレーキ３５、及び、前記第２中間
軸２２に対する第３ブレーキ３６を設け、前記第
１ないし第３クラツチ２６，２７，２８及び第１
ないし第３ブレーキ３３，３５，３６を選択操作
する変速操作装置を設けてある事を特徴とするギ
ヤトランスミツシヨン。 Input shaft 20, first intermediate shaft 21 and second intermediate shaft 2
2 are arranged concentrically, and the reverse cylindrical shaft 23 is attached to the first intermediate shaft 21 and the output cylindrical shaft 24 is attached to the second intermediate shaft 22 so as to be relatively rotatable, and both ends of the spider 25 are attached to the two A first clutch 26 is mounted between the input shaft 20 and the first intermediate shaft 21, and a second clutch is mounted between the input shaft 20 and the reverse cylinder shaft 23. 27
and the second intermediate shaft 22 and the output cylinder shaft 24
A third clutch 28 is provided between the first and second intermediate shafts 21 and 22, respectively.
Third and fourth external gears 29 and 30, which are always engaged with the second external gears 21a and 22a, respectively, are attached to the spider 25 so as to be relatively rotatable, and third and fourth external gears 29 and 30, which are respectively fixed to the two cylindrical shafts 23 and 24, are attached to the spider 25 so as to be relatively rotatable. 5th and 6th
Seventh and eighth external gears 31 and 32, which engage the external gears 23a and 24a separately and engage the third and fourth external gears 29 and 30, respectively, are attached to the spider 25 so as to be relatively rotatable. , a first brake 33 for the reverse cylindrical shaft 23, and an internal gear 34 that constantly meshes with the third external gear 29.
A second brake 35 for the second intermediate shaft 22 and a third brake 36 for the second intermediate shaft 22 are provided, and the first to third clutches 26, 27, 28 and the first
A gear transmission characterized by being provided with a speed change operation device for selectively operating the first to third brakes 33, 35, and 36.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1982013383U JPS58116848U (en) | 1982-02-01 | 1982-02-01 | gear transmission |
| US06/451,369 US4513636A (en) | 1982-02-01 | 1982-12-20 | Gearing transmission |
| CA000418256A CA1190062A (en) | 1982-02-01 | 1982-12-21 | Gear transmission |
| GB08236523A GB2115088B (en) | 1982-02-01 | 1982-12-22 | Gearing transmission |
| FR8222135A FR2520825B1 (en) | 1982-02-01 | 1982-12-30 | TRANSMISSION TO PLANETARY GEARS HAVING SIX FRONT GEARS AND TWO REAR GEARS FOR EARTHMOVERS AND THE LIKE |
| DE3302737A DE3302737C2 (en) | 1982-02-01 | 1983-01-27 | Planetary coupling gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1982013383U JPS58116848U (en) | 1982-02-01 | 1982-02-01 | gear transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58116848U JPS58116848U (en) | 1983-08-09 |
| JPS628453Y2 true JPS628453Y2 (en) | 1987-02-27 |
Family
ID=11831566
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1982013383U Granted JPS58116848U (en) | 1982-02-01 | 1982-02-01 | gear transmission |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US4513636A (en) |
| JP (1) | JPS58116848U (en) |
| CA (1) | CA1190062A (en) |
| DE (1) | DE3302737C2 (en) |
| FR (1) | FR2520825B1 (en) |
| GB (1) | GB2115088B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008151443A1 (en) * | 2007-06-15 | 2008-12-18 | Magna Powertrain Inc. | Dual clutch transmission with planetary gearset |
| CN102767195B (en) * | 2012-07-12 | 2014-08-27 | 太原科技大学 | Working device of synchronous transmission gear type loader |
| CN109654182B (en) * | 2019-02-21 | 2023-07-21 | 威海团中变速器有限公司 | Continuously variable transmission |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3004446A (en) * | 1956-05-25 | 1961-10-17 | Borg Warner | Transmission controls |
| US3314307A (en) * | 1963-12-05 | 1967-04-18 | Gen Motors Corp | Transmission |
| US3274858A (en) * | 1964-01-17 | 1966-09-27 | Deere & Co | Transmission |
| US3298252A (en) * | 1964-01-17 | 1967-01-17 | Deere & Co | Transmission |
| US3446094A (en) * | 1966-06-20 | 1969-05-27 | Nissan Motor | Torque split-type automatic speed change device |
| US3411382A (en) * | 1966-07-15 | 1968-11-19 | Nissan Motor | Five stage automatic speed change device |
| US3489037A (en) * | 1966-07-30 | 1970-01-13 | Nissan Motor | Automatic speed change device for vehicles |
| JPS4820658B1 (en) * | 1970-02-03 | 1973-06-22 | ||
| JPS4820652B1 (en) * | 1970-02-13 | 1973-06-22 | ||
| US3859871A (en) * | 1970-06-02 | 1975-01-14 | Toyota Motor Co Ltd | Speed change gear device |
| US4043225A (en) * | 1973-12-29 | 1977-08-23 | Aisin Seiki Kabushiki Kaisha | Power shift transmission for motor vehicles |
| GB2023752B (en) * | 1978-06-24 | 1982-07-28 | Brown Gear Ind | Variable-speed gearbox |
| FR2483552A1 (en) * | 1980-05-30 | 1981-12-04 | Soma Minerva Procedes Etudes | PERFECTED GEARBOX FOR HIGH POWER VEHICLES |
| FR2484588A1 (en) * | 1980-06-11 | 1981-12-18 | Renault | AUTOMATIC GEARBOX WITH FOUR-SPEED FRONT AND TWO-REVERSE SPEEDS |
-
1982
- 1982-02-01 JP JP1982013383U patent/JPS58116848U/en active Granted
- 1982-12-20 US US06/451,369 patent/US4513636A/en not_active Expired - Fee Related
- 1982-12-21 CA CA000418256A patent/CA1190062A/en not_active Expired
- 1982-12-22 GB GB08236523A patent/GB2115088B/en not_active Expired
- 1982-12-30 FR FR8222135A patent/FR2520825B1/en not_active Expired
-
1983
- 1983-01-27 DE DE3302737A patent/DE3302737C2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| US4513636A (en) | 1985-04-30 |
| DE3302737A1 (en) | 1983-09-29 |
| FR2520825A1 (en) | 1983-08-05 |
| CA1190062A (en) | 1985-07-09 |
| GB2115088A (en) | 1983-09-01 |
| DE3302737C2 (en) | 1986-11-13 |
| JPS58116848U (en) | 1983-08-09 |
| GB2115088B (en) | 1985-08-29 |
| FR2520825B1 (en) | 1985-07-19 |
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